DE4416989C2 - Device for converting a circular movement into a reciprocating movement and vice versa - Google Patents

Abstract

The present invention describes an apparatus for conversion of a circular motion, characterized by comprising: a lever member (103, 125a, 125b, 126a, 126b, 133, 148, 103A, 103B, 103C) having a fulcrum (104, 123, 124, 135) as well as an action point (112) and a force point (102, 132) rotatably mounted at a point on a line connecting a rotational center and a circumference of a rotary body (100, 121, 122, 131, 141, 100A, 100B, 100C), the fulcrum being provided with a regulator (106, 107, 135) for functioning the fulcrum as a movable fulcrum, wherein the regulator includes a pair of guide plates (106, 107, 146, 147) for supporting the fulcrum to be movable in a longitudinal direction of the lever member and a roller (105, 145) which is pivoted to the fulcrum. <IMAGE>

Description

The present invention relates first of all common a device for converting a circle shaped movement in a reciprocating motion and vice versa. An application is used for conversion the reciprocation of, for example, a Kol a four-stroke reciprocating engine into the rotary motion of a crankshaft.

From FR 12 50 455 is a device for order conversion of a circular movement into a back and forth Movement known when working on an engine a rotating body is attached to which a lever link is coupled by means of a force point, with another turn in a guide link Point is provided as a movable lever The fulcrum for the lever acts while on the end of the lever member go back and forth en performs a toothbrush movement. The got te device only serves to convert egg a slight rotary motion into a vibration of the Toothbrush. For converting larger torques te in a reciprocating motion is theirs Device not suitable.

FR 605 474 discloses a lever member with a Lever pivot point, which is in a guide member is, points of action that go back and forth moving pistons are connected, and a force point that is connected to a rotating body. It lacks any special leadership structure, which enables the transfer of larger forces.

In DE-PS 3 30 887 a device for Conversion of a circular movement into one Pivotal movement of a lever member shown at which changes the position of the fulcrum to vary a range in which the Action point shifted when pivoting the lever member can be used.

The present invention therefore relates to be especially on a device for converting a circular motion in a reciprocating motion and vice versa using a lever link with a force point, a fulcrum and a point of action. The power point is rotatable a point arranged on a line that a Center of rotation with a circumference of a rotating body connects, the fulcrum with a he Most guide member is provided so that the lever pivot acts as a movable fulcrum, and the point of action with a move back and forth body is connected. Finally heard to the genus of the invention that the first guide member has support elements to the lever rotation point so that it is in the longitudinal direction of the Lever member can be moved.  

One of the factors that increase the out power output of a four-stroke reciprocating engine is, as is well known, the inevitable lateral end give way to a piston. This side dodging can not be avoided because the piston and the cure Belwelle connected to each other via a connecting rod are. In particular, this lateral loss increases give way as the reciprocation of the piston is not transmitted evenly to the crankshaft, which translates into a loss of energy.

In this way the crank movement intervenes conventionally when converting a linea movement into a rotating movement. However, since the piston when the crankshaft moves, for example wise vibrates in a four-stroke reciprocating engine, tre through the side between the piston and the cylinder evasive forces. Therefore, the Engine idling speed to approx. 1000 revolutions gen per minute, which also becomes a pro leads to fuel consumption.

Dodging sideways creates an energy loss. In addition, the piston must be made from a heavy metal be made of solid metal to prevent damage supply of the piston, e.g. B. cracks, partial breaks and the like in the piston caused by a collision of the Piston with the inner wall of the cylinder other. Then it is not possible to determine the weight of the col bens by producing this from, for example, a reduce ceramic material.

The present invention is therefore the Task based on a device of the above Genus for conversion a circular motion in a back and forth Movement and vice versa with a better one To provide guidance.

In addition, one is said to convert the back and forth Movement of the piston, for example one Four-stroke reciprocating engine in the rotary motion of the Crankshaft energy loss is reduced and the weight of the engine by making the Kol bens made of a ceramic material the.

The general solutions to the task are the claims according to the present invention Chen 1, 3, 4 and 7.  

According to the essence of the present invention a lever with a fulcrum as well a force point and an action point are available provided, one of which is rotatable and axially on one Line is arranged, which is a center of rotation with a Connects the circumference of a rotating body. One who has strength point, or the point of action, is with a first lead provided. The fulcrum is then with provided a second guide member so that the He lever pivot serves as a movable lever pivot. The first leader is with a back and forth coupled body, and the first and the second guide member is with support elements for such camps of either the force or the action point and the fulcrum that he in a longitudinal direction of the lever can be moved.

More details, features and advantages ben from the following description of the drawing, shown in the embodiments of the invention are and the explanation of the principle of the invention serve.

Show it:

Fig. 1 is a perspective view showing an approximate shape exporting to the present invention,

Fig. 2 is a diagram schematically illustrating an example of the geometric standpoint locations of FIG. Connected, rotating and reciprocates reciprocating parts shown 1,

Fig. 3 is a diagram schematically illustrating a different example of the loci of FIG. Shown with affiliated, rotating and moves back and herbewe constricting parts 1,

Fig. 4 is a schematic elevation view of another embodiment of the present invention,

Fig. 5 is a schematic perspective view of a still white direct embodiment of the present invention,

FIGS. 6A and 6B curves which illustrate the operations of the embodiment shown in Fig. 5,

Fig. 7 is a view of a more concrete exporting approximate shape of the Implementing schematically shown in Fig. 5 approximate shape,

Fig. 8 is a plan view of the embodiment of Fig. 7,

FIG. 9 is a transverse view, partly in section, of the embodiment shown in FIG. 7;

Fig. 10 is an elevational view of the embodiment of FIG. 7,

Fig. 11 shows a schematic partial section of another embodiment of the present invention,

Fig. 12 is a schematic partial sectional view of a comparison with FIG. 11 modified embodiment,

Fig. 13 is a schematic elevational view of a still further embodiment of the invention,

FIG. 14A and 14B are schematic elevational views of two sides of a further embodiment of the present invention,

Fig. 15 is a schematic view of yet another embodiment of the present invention,

Fig. 16 is a schematic elevation of a still further embodiment of the present invention,

Fig. 17 is a schematic elevation of a still further embodiment of the present invention,

Fig. 18 is a schematic elevation of a still further embodiment of the present invention,

Fig. 19 is a schematic elevation of a still further embodiment of the present invention,

FIG. 20A and 20B are schematic Seitenan- and top views of yet another embodiment of the present invention,

Fig. 21 shows a schematic section of a still further embodiment of the present invention, and

Fig. 22 shows a schematic section of another exporting approximately of the present invention.

The preferred embodiments of the present invention are now described in detail with reference to the accompanying Described drawings.

FIG. 1 is a schematic perspective view illustrating the overall arrangement of an embodiment of the present invention. This embodiment has a lever 5 , in one end 4 force is applied via a pin. The pin 4 is located near the periphery of a disc 3 which is fixed on a rotating shaft 2 of a motor 1 .

A fulcrum 6 a of the lever 5 is rotatably supported by a fulcrum guide member 6 so that the fulcrum 6 a can move in a longitudinal direction. The fulcrum 6a is such reali Siert by a pin in the lever 5, that the lever is mounted via the pin 6 a b in a rotatably arranged on the lever 5 Roller 6. 5 The guide member 6 consists of the roller 6 b and the roller 6 b above and below leading plates 6 c and 6 d. As a result, the lever 5 can be moved in the longitudinal direction in the guide member 6 .

At the other end of the lever 5 there is also another guide element 7 . The guide member 7 has a roller 7 b, which is rotatably attached via a pin 7 a to the other end of the lever 5 , and top and bottom guide plates 7 c and 7 d for guiding the roller 7 b, so that the roller 7 b and the axis of the pin 7 a can be moved in the longitudinal direction of the lever 5 .

The guide element 7 is arranged essentially in the central section of a cylindrical piston 8 , and the piston 8 is located in a cylinder 9 . (Not shown) Kol benrings are provided on peripheral portions near both Endab sections of the piston 8 to seal an annular gap between the piston 8 and the inner wall of the cylinder 9 .

Inlet and outlet pipes 10 a and 10 b and 10 c and 10 d are arranged in pairs on the two end faces of the cylinder 9 , and opening / closing valves 11 a, 11 b, 11 c and 11 d are provided in the corresponding pipes.

In this arrangement, when the motor 1 is connected to a power supply and is driven, a disc 3 is moved, for example, in the direction of an arrow A shown in FIG. 1, and the lever 5 is repeated every half rotation of the disc 3 counterclockwise or clockwise swiveling movements. Accordingly, the support point represented by the pin 7 a of the lever 5 in the guide element 7 reacts when the disc 3 rotates with a back and forth movement in the direction perpendicular to its longitudinal extent.

The back and forth movement of the pin 7 a of the lever 5 is transmitted to the guide element 7 and accordingly the piston 8 performs a linear back and forth movement in the cylinder 9 . At the same time, the roller 7 b is guided so that it can be moved in the longitudinal direction of the lever 5 along the guide plates 7 c and 7 d of the guide element 7 .

In this case, when the valves 11 a d to 11 opened on movement of the piston 8 in response to the vertical movement of the He bels 5 at predetermined times and closed who the a liquid from the tubes 10 a and 10 c in the Zy Linder 9 are transmitted and are expelled from the tubes 10 b and 10 d.

Since the lateral deflection of the piston 8 in the direction of the inner wall of the cylinder 9 does not seem to be due to the guides 6 and 7 , and the lateral deflection of the lever 5 on the guide plates 6 c, 6 d, 7 c and 7 d to what at the movable lever fulcrum 6 a and a point of action of the pin 7 a of the lever 5 is caused when rotation of the rollers 6 b and 7 b is absorbed, mechanical losses at these sections are very low at this time.

The device according to the embodiment shown in FIG. 1 is a reversible device. For example, if a medium under high pressure such as a liquid or gas or air is alternately supplied from the tubes 10 a and 10 c to move the piston 8 vertically with the medium under high pressure, and the reciprocation of the Piston 8 is transmitted to the disk 3 via the lever 5 in order to rotate the disk 3 , then the motor 1 can be operated in reverse as an engine, for example as a power generator.

Also in this case, since the lateral deflection of the piston ben 8 towards the inner wall of the cylinder 9 and that of the lever 5 towards the guide plates 6 c, 6 d, 7 c and 7 d, what is at the movable fulcrum 6th a and the force application point 7 a of the lever 5 is caused by the back and forth movement of the piston 8 , as rotation of the rollers 6 b and 7 b of the guide members 6 and 7 is absorbed, the mechanical losses at these sections are very small.

Figs. 2 and 3 show the geometric locations of the points 4, 6 and 7 a a during the movement of the embodiment shown in FIG. 1. The pin 4 performs a full circular movement, the fulcrum 6 a moves linearly between the guide plates 6 c and 6 d in the longitudinal direction of the lever 5 , and the pin 7 a moves between the guide plates 7 c and 7 d as Responding to the reciprocation of the piston 8 to form a geometric location as shown in Fig. 2 or 3. The difference in the geometric location of the pin 7 a between FIGS. 2 and 3 is caused by the different position of the pin 6 a of the movable fulcrum. In addition, the stroke of the piston can be varied by different lengths of the lever 5 right and left of the fulcrum 6 a.

Fig. 4 is an elevation showing the schematic arrangement of an embodiment in which the present invention is used in conjunction with a four-stroke engine. An intake pipe 21 , an exhaust pipe 22 , an intake valve 23 and an exhaust valve 24 are provided on the upper portion of a cylinder 20 of the four-stroke engine.

A piston 25 is provided in the cylinder 20 and moves vertically along the inner wall of the cylinder 20 . Although not shown, at least one piston ring is arranged on the outer peripheral surface of the piston 25 to seal the piston 25 with respect to the inner wall of the cylinder 20 . In the piston 25, a guide groove 25 c between a pair of guide plates 25 a and 25 b formed, which form a right angle at a predetermined distance and in a direction to the movement direction of the piston 25 is opposite the groove 25 c.

A role is c 26 with an outer diameter of almost the same size as the width of the guide groove 25 in the guide groove employed c 25th The roller 26 is rotatably attached at one end or force point of a lever 28 via a pin 27 . The plates 25 a, 25 b and the roller 26 act as a force point guide element.

The lever 28 is mounted in a movable lever pivot guide member 29 , the arrangement of which is identical to that of the embodiment shown in FIG. 1. That at the other end of the lever 28 is rotatably connected via a pin 30 to a crankshaft arm of a crankshaft 32 or the peripheral portion of a rotatable disc 31 coupled. The guide member 29 of the movable fulcrum is formed by a pin 28 a, a roller 28 b and guide plates 28 c and 28 d. The guide plates 28 c and 28 d are provided along the direction of reciprocation of the piston 25 , and the roller 28 b is also supported so that it can be moved in the direction of the reciprocation of the piston 25 .

In this embodiment, when a fuel-air mixture is ignited by a spark plug 33 near the top dead center in the compression stroke of the piston 25, the piston ben 25 is pushed down by the explosion of the fuel-air mixture. This pressure is transmitted through the roller 26 and the pin 27 to the lever 28 and then transmitted from the crankshaft arm or disc 31 to the central axis of the crankshaft 32 .

In the embodiment according to FIG. 4, the piston 25 is pushed against the inner wall of the cylinder 20 by the explosion pressure. Since the piston 25 and the lever 28 are coupled together by the guide member consisting of the plates 25 a and 25 b and the role serving as a force point guide element and by the guide member 29 which serves as a guide for the movable lever pivot point, the the piston 25 urging force fully transmitted to the crankshaft 32 and receives no counteraction from the lever 28 , so that since evacuation Liche piston engine is significantly reduced compared to a conventional stroke. Similarly, the fulcrum 28 a of the lever 28 is supported by the guide member 29 of the movable fulcrum, and accordingly the reciprocation of the piston 25 is converted into a rotary motion with little mechanical loss.

In this case, since the piston 25 is not pressed against the inner wall of the cylinder 20 by a large force, the majority of the piston 25 can be made of a ceramic material, for example. Since the lateral evasion is reduced, the energy loss is reduced and the idling speed can be reduced to, for example, 50 revolutions per minute or less, which also has an extremely advantageous effect on fuel consumption.

In the embodiment according to FIG. 5, two cylinders and two pistons, which are each identical to those of the embodiment according to FIG. 4, are coupled coaxially to one another for the sake of the simplified arrangement, as a result of which the efficiency is further improved. Accordingly, in FIG. 5, sections corresponding to those in the arrangement according to FIG. 4 have the same reference numerals and a detailed description thereof is omitted or is given in a simplified manner.

In Fig. 5, pairs of inlet pipes 21 a and 21 b, outlet pipes 22 a and 22 b, and spark plugs 33 a and 33 b are arranged on the two end faces of the cylinder 20 . A piston 25 is inserted in the cylinder 20 and a pin 27 , which serves as a power take-off point, and a roller 26 and guide plates 25 a and 25 b, which serve as a guide member of the power point, are provided in the piston 25 . The pin 27 is attached to one end of a lever 28 and the lever 28 is rotatably coupled via a guide member 29 of the fulcrum 28 a with a crank arm or a force-receiving portion 30 a of a crank shaft 32 . The force-receiving section 30 a corresponds to the pin 30 of the crank disk 31 in the embodiment according to FIG. 4.

In the embodiment shown in FIG. 5, the inlet pipes 21 a and 21 b and the outlet pipes 22 a and 22 b are opened and closed by valves (not shown) at predetermined times. These sections may have the same arrangement as that of a conventional four-stroke engine, and detailed descriptions thereof are therefore omitted.

It is assumed that the crankshaft 32 is rotated by a starter motor (not shown), that the piston 25 is moved in the cylinder 20 . Here it approaches, for example, the left end in Fig. 5 and the fuel-air mixture is compressed at this time. When the fuel-air mixture is ignited by the spark plug 33 a, the piston 25 is pushed to the right in FIG. 5 and the lever 28 is rotated clockwise via the pin 27 and the roller 26 in the guide element of the power take-off point. Upon rotation of the lever 28 in a clockwise direction about the pin 28 a of the fulcrum around which the crankshaft is caused to rotate counterclockwise 32nd As a result, the piston 25 is moved in the cylinder 20 so that the computationally th end in Fig. 5 it approaches, and then the exhaust gas from the pipe 22 is ejected b. If it is intended that an explosion should take place in the second right cylinder, then the crankshaft 32 is rotated continuously. In the four-stroke mode, the second cylinder, in a manner not shown, can be a further cylinder 20 which is connected in the same way to the crankshaft via a further insult.

If an explosion occurs in this second cylinder, not shown, then the piston 25 is moved to the left in Fig. 5 to exhaust the exhaust gas through the pipe 22 a, and at the same time the fuel-air mixture is drawn from the inlet pipe 21 b . Occurs an explosion in a further theoretical third cylinder, when the piston 25 approaches the left end in Fig. 5, the piston 25 around the via the inlet pipe 21 b retracted to compress the fuel-air mixture is moved to the right. The piston 25 is moved in the cylinder 20 so that it approaches the right end in FIG. 5. When the compressed fuel-air mixture is ignited by the spark plug 33 b at this time, the piston 25 is pushed to the left. In this way, the crankshaft 32 is continuously rotated in the direction indicated by an arrow A through a push-pull operation on which two double cylinder act on a crankshaft.

In Fig. 6a the operation of a four-stroke engine is Darge provides, in which two cylinders with the arrangement shown in Fig. 5 are connected to the crankshaft 32 , and in Fig. 6B operations of another two cylinders of the four-stroke engine are shown, in which a total of four cylinders identical to that used in Fig. 5, are arranged to continuously effect four-stroke operation. In this case, if the four cylinders are arranged so that an explosion always takes place by pushing and pulling (or push-pull) processes on both sides of the lever 28 according to FIG quiet motor with low vibration is realized.

In this embodiment, the piston 25 is well balanced on the two sides of the pin 27 and the piston 25 contacts the guide plates 25 a and 25 b of the lever 28 , which replaces the conventional connecting rod, only linearly via the roller 26 . Therefore, during each explosion, the piston 25 does not deviate much laterally onto the inner wall of the cylinder 20 . Accordingly, the energy loss caused by the lateral deflection is small, so that a reciprocating engine with high efficiency is achieved. Since during the lateral evasion not a very large force acts on the piston 25, the piston 25 may be made of a ceramic material.

If the reciprocating piston engine is manufactured using a ceramic material, then the internal temperature of the cylinder 20 can be increased to two to three times that of a conventional engine. It is known that the thermal efficiency of the conventional reciprocating piston engine contributes 20%. In this embodiment, the mechanical loss can also be significantly reduced. For example, if a mechanical loss of 10% can be avoided and if it is assumed that a remaining heat loss can be reduced from 70% to 1/3, then a high efficiency of (10 + 70/3 + 20)%, ie more than 50% can be achieved.

Since the total coefficient of friction from the piston 25 to the crank shaft 32 becomes very small, overall a very uniform movement can be achieved and the idle speed can be reduced to, for example, 50 revolutions per minute or less.

In Figs. 7 to 10 an embodiment of a horizontal right-coaxial four-cycle engine is shown, in which a cylinder having the arrangement of the embodiment of FIG. 5 is arranged horizontally. In Fig. 7, a roller 43 a is inserted in a guide groove 42 a, which is formed between guide plates 42 b and 42 c, which in turn are formed in a piston 41 a, which is inserted in a cylinder 40 a and by a pin 44 a is connected to one end of a lever 45 a.

The roller 43 a, the two guide plates 42 b and 42 c form a force point guide element and the pin 44 a acts as the force point of the lever 45 a.

The lever 45 a is also mounted with a pin 48 a, which acts as a movable fulcrum, namely in a fulcrum guide member consisting of a roller 47 a, which is inserted in a guide groove 46 a. The other end or the point of action of the lever 45 a is coupled to a crank arm 49 a of a crank shaft. The crankshaft arm 49 a is coupled via a belt 61 and rollers 62 a, 62 b, 62 c, 62 d and 62 e, which are shown in FIG. 10 and serve as a coupling member, with camshafts 50 a and 50 b and drives the cams 51 a and 51 b, which sit on the camshafts 50 a and 50 b. The cams 51 a and 51 b control via levers 53 a and 53 b, which guides 52 a and 52 b have movable lever pivot points, valves 54 a and 54 b.

As shown in Fig. 8, in addition to the valve 54 a, another valve 55 a is provided on one side of the cylinder 40 a. The valve 55 a is driven via a lever 56 a similar to the lever 53 a. 8 As further seen in FIG., In addition to the valve 54b, another valve 55 b provided on the other side of the cylinder 40 a. The valve 55 b is driven by a lever 56 b similar to the lever 53 b. Referring to FIG. 8 are pairs of spark plugs 57 a and 57 b and 58 a and 58 b respectively on the two sides of the cylinder 40 a is provided.

Fig. 9 shows a transverse view, partly in section along the portion of the lever 45 a shown in Fig. 7. The Kur belwellenarm 49 a, which is coupled to the lower end of the lever 45 a, is mounted in bearings 60 a and 60 b.

The motor shown in FIGS. 7 to 10 is basically the same as that shown in FIG. 5, and a description of its operation is therefore omitted. In this motor, a lever, which is identical to the lever 28 used between the piston 25 and the crankshaft 32 in FIG. 5, is used in the drive mechanism of the valves 54 a to 55 b, so that the motor can rotate at a higher speed.

Examples of a valve opening / closing mechanism will be described with reference to FIGS . 11 and 12. In Fig. 11, the valve opening / closing mechanism is applied to a poppet valve. A guide groove 71 of a power point guide member is formed at the driven end of a plunger 70 in a direction perpendicular to the direction of movement of the plunger 70 , and a roller 72 is located in the guide groove 71 . The roller 72 is arranged via a pin 73 in the force introduction point of a lever 74 . A valve stem 75 is hinged to the other end of the lever 74 . A movable lever pivot point of the lever 74 is mounted in a roller 77 via a pin 76 . The roller 77 is held by a guide groove 78 of a fulcrum guide member in the motor body 79 so that it can move freely in the longitudinal direction of the lever 74 .

A valve 80 is formed at the other end of the valve stem 75 . An abutment disk 81 is attached to the valve stem 75 . The valve 80 formed at the other end of the valve stem 75 closes constantly an inlet or outlet opening 83 under the action of a spring 82 . The spring 82 is located between the disk 81 and the motor body 79 . The plunger 70 is adjusted so that the motor body 79 acts as an input guide member of the movable force introduction point, and the valve stem 75 is set in that the motor body 79 serves as an output guide member of the articulated connection between the lever 74 and the shaft 75 .

With the valve opening / closing mechanism configured in this way, the vertical movement of the plunger 70 guided by the input guide member of the force point is smoothly transmitted to the valve stem 75 , and the movement of the valve stem 75 is controlled by the output Guide member of the point of action and through a wall 71 a on the upper side of the guide groove 71 , which is formed in the driven end of the plunger 70 . Thus, even with an increase in engine speed, the valve 80 always follows the vertical movement of the plunger 70 without undesired deflections. Therefore, the engine speed can be increased significantly compared to the conventional engine.

Fig. 12 shows an example in which the valve opening / closing mechanism is applied to an overhead cam valve (OHC valve). Fig. 12 differs from Fig. 11 only in that the valve opening / closing mechanism is driven by an overhead cam 85 instead of the plunger 70 and that a guide groove 78 is formed between a guide plate 78 a and a motor body 79 . The operation of this mechanism is basically the same as that of FIG. 11.

All of the above embodiments relate to Devices for converting a rotary movement into a line are float and vice versa. The following executions Forms refer to devices for immediate Conversion of a rotary motion into a back and forth Pivotal movement of a lever.

111 Fig. 13 shows a basic actuator arrangement of such a device. In FIG. 13, a rotor arm 101 A is coupled to a motor 100 via a rotating shaft 101 and is driven by the latter. A lever 103 is coupled to the free end of the rotor arm 101 A by means of pin 102 . A movable fulcrum 104 of the lever 103 is rotatably supported in a roller 105 between a pair of parallel guide plates 106 and 107 of a fulcrum guide member. All of these components are housed in a rectangular, at 108 open housing 109 and in particular the section around the motor 100 is stuffed with a damping filler 110 .

With this arrangement 111, when current is applied to the motor 100 to rotate the shaft 101 , when the motor 100 rotates, the free end of the rotor arm 101 A or the pin 102 will make a circular movement to form a track that is depends on the length of the arm 101 A. Accordingly, the roller 105 is linearly moved between the guide plates 106 and 107 , and the lever 103 swings back and forth about the movable fulcrum 104 as the center. With this arrangement, rotation of the rotary arm 101 A is uniformly converted into the reciprocating motion of the lever 103 . It should be noted that the angle of the reciprocating pivotal movement of the lever 103 can be changed by changing the ratio of the distances between the fulcrum 104 , the force point 102 and an action point 112 .

In FIGS. 14A and 14B, the rotor blades 125 a, 125 b, 126 a, 126 b of an aircraft (or an air combustion engine) gebil det by using two sets of basic arrangements 111, each of which is shown identical to that in Fig. 13 . FIG. 14A shows a plan view and Fig. 14B is a side view. In FIGS. 14A and 14B, rotary disks 121 and 122 are coupled to the rotatable shafts (not shown) motors and are driven by them. The rotary movements of the disk 121 are transmitted to the rotor blades 125 a, 125 b and those of the disk 122 to the rotor blades 126 a, 126 b. On the periphery of the disks 121 and 122 gearing conditions are formed so that the disks 121 and 122 interlock to drive the rotor blades 125 a, 125 b synchronously to the rotor blades 126 a, 126 b. These rotor blades serve as levers via guide members 123 and 124 of the movable lever pivot point and are set in striking movements. In addition to the motors, the disks 121 and 122 can also be operated by a rubber motor attached from the front. In such a case, one end of a twisted rubber belt can be hung on the hook 127 .

Fig. 15 shows a structure in which one end of a lever 133 is coupled via a pin 132 to the peripheral portion of a rotary body 131 . In this case, lever 133 is used as an arm of a crane using a movable fulcrum 135 . A counterweight 134 is provided at the rear end of the lever 133 so that the lever 133 can move balanced as a crane.

In one embodiment of FIGS. 16 and 17, a shaft blunt 143 is connected obliquely with the crank to a rotating shaft of a motor 141 via an angle connection 142 . A rotatable roller 145 , which acts as a moving fulcrum, supports the shaft end 143 and the roller 145 is sandwiched by two parallel guide plates 146 and 147 , which act as a guide member of the movable fulcrum. In this arrangement, the stub shaft 143 describes a conical surface, for which the roller 145 represents the apex. Therefore, if a triangular plate 148 is arranged on this stub shaft 143 , the plate 148 can be operated as a propeller.

FIG. 18 shows an example in which a humanoid (ie, the human foot nachempfundener) foot using three sets of the basic arrangements 111 A, 111 B and 111 C, each shown identical to that in Fig. 13, is formed. In particular, the lower end of a lever member 103 A of the basic arrangement 111 A is attached to a housing 109 B of the basic arrangement 111 B, and the lower end of a lever 103 B of the basic arrangement 111 B is attached to a housing 109 C of the basic arrangement 111 C. If disks 100 A to 100 C of the basic arrangements 111 A to 111 C are driven by motors (not shown), then the corresponding levers 103 A to 103 C are swung to carry out the movement of the humanoid foot, in which the lever member 103 A serves as the femoral area (thigh area), the lever member 103 B as the leg and the lever member 103 C as the foot.

In Fig. 19 shows an example in which a humanoid arm using three sets of the basic arrangements 111 A, 111 B and 111 C is formed, each shown identical to that in Fig. 13. In particular, the lower end of a lever member 103 A of the basic arrangement 111 A is fastened to a housing 109 B of a basic arrangement 111 B, and the lower end of a lever member 103 B of the basic arrangement 111 B is fastened to a housing 109 C of a basic arrangement 111 C. If the disks 100 A to 100 C of the basic arrangements 111 A to 111 C are driven by motors 100 a, 100 B and 100 C, then the respective lever members 103 A to 103 C are swung to carry out the movement of the humanoid arm, whereby the Lever member 103 A acts as an upper arm, the lever member 103 B as an arm and the lever member 103 C as a hand.

FIG. 20A and 20B show still another execution of the present invention, which is formed for example as Gleichgewichtsausbalancierung a robot. Fig. 20A is a side view and Fig. 20B is a plan view. Also in this embodiment, two sets of the basic arrangements 111 A and 111 B are used, both of which are identical to that shown in FIG. 13. The lower end of a lever 103 A of the first basic arrangement 111 A is fastened to the lower end of a fixed arm 151 which extends away from the rear section of a housing 109 B of the second basic arrangement 111 B, at an angle of 90 °. A columnar weight 152 is 103 B of a second basic arrangement 111B mounted on the remote end of a lever. Accordingly, the pivoting direction of the lever 103 A of the first basic arrangement 111 A and that of the lever 103 B of the second basic arrangement 111 B form an angle of 90 °. If this equilibrium balance is attached, for example, to a robot that moves on two legs and the levers 103 A and 103 B of the basic arrangements 111 A and 111 B are pivoted in accordance with the output data of the position sensor of the robot by using the levers 103 A and 103 B by means of of the motors 100 A or 100 B are driven, then a very precisely coordinated position control operation can be carried out as a result.

In Fig. 21, a four-cylinder radial engine according illustrates yet another embodiment of the present invention Darge. In this figure, first and second common cylindrical cylinders 161 and 162 are arranged so that the axes of the cylinders 161 and 162 are parallel to each other. Both ends of the cylinders 161 and 162 are closed by cylinder covers 163 , 164 , 165 and 166 . Two valves 167 a, 167 b are arranged through the cylinder cover 163 . Similarly, the valves 168 a, 168 b, 169 a, 169 b, 170 a and 170 b are arranged through the cylinder covers 164 , 165 and 166 .

First and second pistons 171 and 172 are provided in cylinder 161 and connected to one another via a connecting member 173 . Two guide plates 174 and 175 are provided between the pistons 171 and 172 such that a roller 176 is freely movable between the guide plates 174 and 175 perpendicular to the axial direction of the cylinder 161 . Recesses 171 a and 172 a are formed in the pistons 171 and 172 to reduce their weight, and the open ends of the recesses 171 a and 172 a are closed by piston plates 177 and 178 , so that combustion chambers 179 and 180 between the cylinder covers 163rd , 164 and the piston plates 174 , 175 are formed out. Sealing devices or piston rings 181 are provided for sealing the combustion chambers 179 , 180 at the annular gaps between the pistons 171 , 172 and the cylinder 161 .

Similarly, first and second pistons 185 and 186 are provided in cylinder 162 and connected to one another via a connecting device 187 . Two guide plates 188 and 189 are provided between the pistons 185 and 186 , so that a roller 190 is freely movable between the guide plates 188 and 189 perpendicular to the axial direction of the cylinder 162 . Recesses 191 a and 192 a are formed in the pistons 185 and 186 to reduce their weight, and the open ends of the recesses 185 and 186 are closed by piston plates 192 and 193 , so that combustion chambers 194 and 195 between cylinder covers 165 , 166 and Piston plates 192 , 193 are formed. Sealing devices 196 are provided for sealing the combustion chambers 194 , 195 in a manner similar to that in the cylinder 161 .

The cylinders 161 and 162 are fixed to a frame 200 so that the cylinders 161 and 162 are parallel to each other and a center rod 201 of a crankshaft 202 is in a direction perpendicular to the axes of the cylinders 161 and 162 .

The roller 176 is rotatably mounted on a pin 204 at one end of a lever 203 . The lever 203 is mounted in a movable lever pivot 204 , which is formed by a support roller 204 a via a pin 204 b between guide plates 204 c, 204 d, which act as a guide member of the movable lever pivot to move the lever 203 in the longitudinal direction thereof to store. The other end of the lever 203 is rotatably coupled to a force-absorbing portion of the crankshaft 202 . Similarly, roller 190 is rotatably attached to one end of lever 205 via pin 206 . The lever 205 is carried by a movable lever fulcrum 207 , which is formed by a support roller 207 a via a pin 207 b between guide plates 207 c, 207 d of a guide member of the movable lever fulcrum in order to mount the lever 205 rotatably in its longitudinal direction. The other end of the lever 205 is rotatably coupled to a force-absorbing portion of the crankshaft 202 .

When a spark plug (not illustrated) is set in the combustion chamber 179 under power, this will be initiated, for example, via the valve 167 a into the chamber 179 the fuel-air mixture or combustion gas is ignited and forces pistons 171 and 172 toward the Cylinder cover 164 to compress the combustion gas introduced into the chamber 180 , for example through the inlet valve 168 a. Simultaneous combustion gas is introduced into the chamber 194 and the combustion gas is discharged for example through the drain valve 170 b from the chamber 195th

When the piston 171 is pushed towards the chamber 180 , the roller guided between the plates 174 and 175 is also moved in the same direction and the lever 203 is turned counterclockwise around the pin 204 b of the roller 204 a while the roller 204 a is guided between the plates 204 c and 204 d in the longitudinal direction of the lever 203 , whereby the crankshaft 202 is rotated clockwise around the central rod 201 .

As a result of this process, piston 171 moves to bottom dead center and piston 172 moves to top dead center, where the introduced combustion gas is compressed in chamber 180 . When the compressed combustion gas is ignited in the chamber 180 (not shown) by a spark plug, the piston is pushed 172 towards the cylinder cover 163 on to the lever 203 in the Time gersinn around the movable fulcrum 204 to rotate around to the crankshaft 202 further clockwise, as indicated by arrow A.

Thus, the so-called explosion steps in chambers 179 , 180 , 194 and 195 take place in the order mentioned and so-called four-stroke steps, ie inlet, compression, explosion and outlet steps are carried out in each of the chambers 179 , 180 , 194 and 195 in order to to continuously rotate the crankshaft 202 .

According to the embodiment of FIG. 21, it is possible to form a four-cylinder engine using two cylinders 161 and 162 , which enables the size, weight and volume of the reciprocating engine to be reduced.

Furthermore, since the piston movement is transmitted to the crankshaft using the lever 203 of the movable fulcrum type, there is no lateral deflection of the pistons 171 , 172 , 185 and 186 with respect to the inner wall of the cylinders 161 and 162 , thereby causing the piston to move is transmitted very smoothly to reduce energy loss. Accordingly, it is possible to reduce the idle speed from 1000 revolutions per minute to, for example, 50 revolutions per minute. Furthermore, since the levers 203 and 205 can be made to have the same length with each other, it is possible to design the distance from the axis of the cylinder 161 to the center of the crank shaft 201 to be equal to that between the axis of the cylinder 162 and the center of the rod 201 is to reduce the vibration of the four-stroke reciprocating engine.

Furthermore, since there is no lateral deflection of the pistons 171 , 172 , 185 and 186 with respect to the inner wall of the cylinders 161 and 162 , it is possible to design the pistons as ceramic pistons, thereby reducing the weight of the pistons and the overall weight of the engine.

FIG. 22 shows an 8-cylinder radial engine, which is designed according to the present invention, in which two sets of the four-cylinder engine according to FIG. 21 are combined and form the 8-cylinder reciprocating engine. The 8-cylinder engine according to FIG. 22 may be performed using four cylinders 161, 162, 261 and 262 are formed. The cylinders 161 and 162 have the same structure as those shown in FIG. 21. Therefore, explanations of the structure regarding the cylinders 161 and 162 and the cylinders 261 and 262 can be omitted here except for the fact that the levers 203 and 205 with a crank arm 202 a and the levers 403 and 405 b with a further crank arm 202, the center of the crankshaft rod 201 is located with respect to 180 degrees from the arm 202 a distance, are connected.

Operations of the 8-cylinder reciprocating engine will now be described. In Fig. 22, step 171 of the explosion, the piston as a result in the combustion chamber 179 in the cylinder 161 at its bottom dead center. At the same time, the piston 185 is located as a result of the explosion step in the combustion chamber 194 in the cylinder 162 also at its bottom dead center. At this point, the chambers 180 and 195 are in the final stage of the compression stroke, while the pistons 271 , 272 , 285 and 286 are in the central position in the cylinders 261 and 262 , respectively.

If the compressed fuel gas in the chambers 180 and 195 is ignited by spark plugs (not shown), the levers 203 and 205 are moved clockwise and counterclockwise, respectively, and rotate the crankshaft rod 201 in the direction indicated by arrow A. Accordingly, the levers 403 and 405 rotate clockwise and counterclockwise, respectively, and compress the fuel gas in the chambers 280 and 295 and the fuel gas is introduced into the chambers 279 and 294 , respectively.

According to the present embodiment of FIG. 22, all levers 203 , 205 , 403 and 405 can be manufactured identically, so that the overall structure of the 8-cylinder engine is symmetrically shaped with respect to the central rod 201 of the crankshaft, whereby the engine vibrates further is wrestled.

As described in detail above, according to present invention an apparatus for converting a circular motion in a reciprocating motion and vice versa returns to be made available which is an energy loss can decrease if they float from at for example, the piston of a four-stroke reciprocating engine in the Implements rotary motion of a crankshaft, and that by using a ceramic material as a material for the manufacture tion of the device can be reduced in weight.

Claims (11)

1. A device for converting a circular movement into a reciprocating movement and vice versa using a lever member with a force point, a lever pivot point and an action point,
in which the force point is rotatably arranged at a point on a line connecting a center of rotation with a periphery of a rotating body, the fulcrum being provided with a first guide member so that the fulcrum functions as a movable fulcrum and the point of action with itself floating body is connected; and
wherein the first guide member has support elements to support the fulcrum so that it can be moved in the longitudinal direction of the lever member, characterized in that
that the first guide member of the fulcrum ( 6 a) has a roller ( 6 b) which is rotatably attached to the fulcrum ( 6 a), and a pair of guide plates ( 6 c, 6 d) for guiding the roller ( 6 b) in one groove formed between the guide plates ( 6 c, 6 d);
that the point of action ( 7 a) is provided with a second guide member which is connected to the reciprocating body by ( 8 ), the second guide member having a roller ( 7 b) which is rotatable at the point of action ( 7 a) BEFE Stigt, and a pair of guide plates ( 7 c, 7 d), which are attached to the reciprocating body ( 8 ) to the roller ( 7 b) in a between the guide plates ( 7 c, 7 d) trained groove in the longitudinal direction of the lever member to guide, and
that when the rotating body ( 3 ) rotates about its rotating shaft ( 2 ), the lever member ( 5 ) swings around the fulcrum ( 6 a) in order to linearly drive the reciprocating body ( 8 ) while the action point ( 7 a ) describes a curved locus. 2. Device according to claim 1, characterized in that
that the reciprocating body has a piston ( 8 ) inserted into a cylinder ( 9 ) such that the piston ( 8 ) moves freely from one end to the other end of the cylinder ( 9 ) to fill gaps between the Kol ben ( 8 ) and the inner wall of the cylinder ( 9 ) to form;
that tubes ( 10 a, 10 c) and valves ( 11 a, 11 c) are provided, which enable a liquid alternately into the at the movement of the piston ( 8 ) from one end to the other end of the cylinder ( 9 ) both ends of the Zylin ders ( 9 ) formed gaps is added, and
that tubes ( 10 b, 10 d) and valves ( 11 b, 11 d) are provided which enable the liquid absorbed into the gaps when the piston ( 8 ) moves from one end to the other end of the cylinder ( 9 ) alternately ejected from the gaps. 3. A device for converting a circular movement into a reciprocating movement and vice versa using a lever member with a point of force, a fulcrum and a point of action;
in which the action point is rotatably arranged at a point on a line connecting a center of rotation with a periphery of a rotating body, the fulcrum being provided with a first guide member so that the fulcrum acts as a movable fulcrum and the power point with itself floating body is connected; and
the first guide member has support members to support the fulcrum so that it is movable in a longitudinal direction of the lever member; characterized,
that the first guide member of the fulcrum ( 28 a) has a roller ( 28 b) which is rotatably attached to the fulcrum ( 28 a), and a pair of guide plates ( 28 c, 28 d) for guiding the roller ( 28 b) in one formed between the guide plates ( 28 c, 28 d) groove;
that the force point ( 27 ) is provided with a second guide member which is fixed to the reciprocating body ( 25 ), the second guide member having a roller ( 26 ) which is rotatably attached to the force point ( 27 ), and a pair of guide plates ( 25 a, 25 b) which are connected to the reciprocating body ( 25 ) to guide the roller ( 26 ) in a groove formed between the guide plates ( 25 a, 25 b) , and
that when the reciprocating body ( 25 ) is linearly driven in a guide member ( 20 ), the point of force ( 27 ) in the groove ( 25 c) moves in a longitudinal direction of the lever member and writes a closed locus, so that the rotating body ( 31 ) is driven such that it rotates around its rotating shaft ( 32 ) ( Fig. 5). 4. A device for converting a circular motion into a reciprocating motion and vice versa using a reciprocating engine with a power point, a lever fulcrum and an effective point, wherein a reciprocating piston arranged in a cylinder is coupled with a cure belwelle by a connecting mechanism is characterized by
that the connecting mechanism has a lever member ( 28 ) with a force point ( 27 ), a lever pivot point ( 28 a) and an action point;
that the action point is rotatably attached to the crankshaft ( 32 ), the fulcrum ( 28 a) is provided with a first guide member ( 29 ) to form the fulcrum ( 28 a) as a movable fulcrum, and the force point ( 27 ) with the Piston ( 25 ) is coupled,
that the first guide member ( 29 ) of the fulcrum ( 28 a) has a roller ( 28 b) which is rotatably attached to the fulcrum ( 28 a), and a pair of guide plates ( 28 c, 28 d) for guiding the roller ( 28 b ) in a between the Füh guide plates ( 28 c, 28 d) formed groove;
that the force point ( 27 ) is provided with a second guide member which is attached to the piston ( 25 ), the second guide member having a roller ( 26 ) which is rotatably attached to the force point ( 27 ), and a pair of guide plates ( 25 a, 25 b) which are attached to the piston ( 25 ) to guide the roller ( 26 ) in a groove formed between the guide plates ( 25 a, 25 b), and
that when the piston ( 25 ) in the cylinder ( 20 ) is linearly driven, the point of force ( 27 ) in the groove formed between the guide plates ( 25 a, 25 b) in a longitudinal direction of the lever member moves to a closed locus describe so that the crankshaft arm ( 30 a) is driven such that it rotates around its rotary shaft ( 32 ). 5. The device according to claim 4, characterized in
that the piston ( 25 ) is inserted into the cylinder ( 20 ) such that the piston ( 25 ) moves freely from one end to the other end of the cylinder ( 20 ) to fill gaps between the piston ( 25 ) and the inner wall of the To form cylinders ( 20 );
that inlet units ( 21 a, 21 b) are provided, via which a fuel-air mixture in the gaps, which in the movement of the piston ( 25 ) from one end of the cylinder ( 20 ) to the other alternately at both ends of the cylinder ( 20 ) be formed, introduced;
that outlet units ( 22 a, 22 b) are provided, via which a combustion gas which arises in the gaps is expelled alternately from the gaps when the piston ( 25 ) moves from one end of the cylinder ( 20 ) to the other; and
that devices ( 33 a, 33 b) are provided for igniting the compressed fuel-air mixture in the gaps formed at the ends of the cylinder ( 20 ) alternately. 6. The device according to claim 5, characterized in that the inlet and the outlet units ( 21 a, 21 b, 22 a, 22 b) valves ( 80 ) for opening / closing inlet and outlet openings ( 83 ) of the cylinder ( 20th ) have, with these valves coupled actuating arms ( 74 ) and to drive units for driving the valves by means of the actuating arms, the actuating arms having drive units coupled to the drive units having guide members ( 71 a, 72 ) for the force point ( 73 ), coupled to the valves Action point guide members, and guide members ( 77 ) for the movable fulcrum, and the guide members for the power point and the movable fulcrum have support members which pivot the power point and the movable lever so that they are movable in a longitudinal direction of the operating arms. 7. radial engine having a plurality of motor base units which are mounted radially around an exhaust axis, each of the motor base units being provided for converting the reciprocating motion into a circular movement of the exhaust axis and vice versa, each of the motor base units ten includes:
a rotating body connected to the outlet axis;
a reciprocating piston engine having a cylinder head cylinder having inlet and outlet units for a fuel gas and an ignition unit, and a piston body which is inserted in the cylinder; and
a connecting mechanism for connecting the piston body to the rotating body to convert the reciprocation of the piston into the circular movement of the rotating body and vice versa the rotating movement into a reciprocating movement of the piston; characterized,
that the cylinder has two cylinder heads, each of which is provided with intake and exhaust units ( 167 a, 167 b, 168 a, 168 b, 169 a, 169 b, 170 a, 170 b) for the fuel gas and an ignition unit;
that the piston body comprises two piston members ( 171 , 172 , 185 , 186 , 271 , 272 , 285 , 286 ) which are inserted into the cylinder ( 161 , 162 , 261 , 262 ) facing the first and the second end section;
that the link mechanism includes a lever member ( 203 , 205 , 403 , 405 ) having a force point, a fulcrum, and an action point;
that the action point is rotatably attached to a crankshaft arm ( 202 a, 202 b) of the crankshaft rod ( 201 ) which functions as the rotating body;
that the fulcrum ( 204 b, 207 b) is provided with a first guide member to form the fulcrum as a movable lever fulcrum, and the force point ( 204 , 206 ) with the piston members ( 171 , 172 , 185 , 186 , 271 , 272 , 285 , 286 ) is coupled;
that the first guide member has support members ( 204 c, 204 d, 207 c, 207 d) for supporting the fulcrum so that it is movable in a longitudinal direction of the lever member ( 203 , 205 , 403 , 405 );
that the first guide member of the fulcrum has a roller ( 204 a, 207 a) which is rotatably attached to the fulcrum ( 204 b, 207 b), and a pair of guide plates ( 204 c, 204 d, 207 c, 207 d) to guide the roller ( 204 a, 207 a) in a groove formed between the guide plates;
that the force point ( 204 , 206 ) is provided with a second guide member which is fastened to the piston members ( 171 , 172 , 185 , 186 , 271 , 272 , 285 , 286 ), the second guide member having a roller ( 176 , 190 ) which is rotatably attached to the force point ( 204 , 206 ) and a pair of guide plates ( 174 , 175 , 188 , 189 ) which are connected to the piston members ( 171 , 172 , 185 , 186 , 271 , 272 , 285 , 286 ) connected to guide the roller ( 176 , 190 ) in a groove ( 173 , 187 ) formed between the guide plates; and
that when the piston members ( 171 , 172 , 185 , 186 , 271 , 272 , 285 , 286 ) are linearly driven in the cylinders ( 161 , 162 , 261 , 262 ), the force point ( 204 , 206 ) in the groove ( 173 , 187 ) moved in a longitudinal direction of the lever member ( 203 , 205 , 403 , 405 ) to describe a closed locus, so that the crankshaft arms ( 202 a, 202 b) are driven such that they rotate around the crankshaft ( 201 ) turn around. 8. Use of the device for converting a rotary movement into a back and forth movement according to one or more of the preceding claims, characterized in that the back and forth movement is used to propel a vehicle in a medium such as air or water ( Fig. 14A, 14B, 16 and 17). 9. Using the device for converting a back and forth Movement in a rotary motion after one or more of the preceding claims, characterized, that the float from a naturally flowing Medium such as air or water is excited. 10. Use of the device for converting a rotary movement into a reciprocating movement and vice versa according to one or more of the preceding claims, characterized by the controllable balancing of a load ( Fig. 15, 20A and 20B). 11. Use of the device according to one or more of the preceding claims, characterized in that the rotary movement is converted into a reciprocating movement, which is modeled on the movement of human limbs ( Fig. 18 and 19).